U.S. patent number 6,979,185 [Application Number 09/916,091] was granted by the patent office on 2005-12-27 for bi-rotational pump/hydraulic actuator.
Invention is credited to Staffan I. Kaempe.
United States Patent |
6,979,185 |
Kaempe |
December 27, 2005 |
Bi-rotational pump/hydraulic actuator
Abstract
A novel bi-rotational pump adapted to pump fluid in either of
two directions by reason of construction inclusive of passageways
and an array of check valves and pilot pistons which cooperate in
one direction and in another way in the other direction.
Inventors: |
Kaempe; Staffan I. (Paoli,
IN) |
Family
ID: |
26916651 |
Appl.
No.: |
09/916,091 |
Filed: |
July 26, 2001 |
Current U.S.
Class: |
418/131; 418/133;
418/206.1; 418/206.4; 60/475; 60/476 |
Current CPC
Class: |
F04C
14/04 (20130101) |
Current International
Class: |
F03C 002/00 () |
Field of
Search: |
;418/131,132,206.1,133,206.4 ;60/475,476 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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|
|
|
|
|
350877 |
|
Jan 1961 |
|
CH |
|
60-75783 |
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Apr 1985 |
|
JP |
|
Primary Examiner: Trieu; Theresa
Attorney, Agent or Firm: Stutz; Paul F.
Parent Case Text
The inventions disclosed herein are disclosed and described in a
prior Provisional Application entitled "DEVICE/SYSTEM FOR MOVING
FLUIDS", filed Aug. 1, 2000 and identified as Ser. No. 60/222,290.
Applicant expresses herein his intention that the present
Application may rely upon the filing date of Aug. 1, 2000 of his
Provisional Application as a priority date for all purposes.
Claims
What is claimed is:
1. An improved bi-rotational gear pump generally comprising a
generally circular or annular gear housing defining a central
cavity; adapted and sized to receive a pair of intermeshing gears
carried axially by drive means, rotating in a "cw" or "ccw"
direction and thereby pumping liquid through said pump depending
upon the rotation of said drive means, a pair of generally circular
cover members situated concentrically in flush abutment, on either
side of said gear housing, a pair of generally circular end-cap
members in concentric flush abutment on either side of said cover
members; said cover members and said end cap members each being
machined so as to define together a plurality of interconnected,
internal passageways, an inlet means for fluid leading to said pair
of intermeshing gears, and two outlet means for pumped fluid and
means for directing said fluid to one or other of said outlet means
depending on the direction of rotation of said intermeshing
gears.
2. The invention as claimed in claim 1 wherein the series of
connected internal passageways includes an array of ball valves
which are constructed and arranged to open or close depending upon
the rotational movement of the intermeshing gears and consequent
movement of the fluid.
3. The invention as claimed in claim 2 and further comprising a
plurality of valves located within said connected internal
passageways and means for controlling said ball valves as to change
the movement of said fluid through internal passageways.
4. The invention as claimed in claim 3 and further comprising a
pilot type piston located in at least one of the valves serving to
open or close the valve in question.
Description
BACKGROUND
The present inventions relate to novel mechanisms, and, as well,
systems for moving fluids in a controllable, precise, accurate and
advantageous fashion, generally for the purpose of developing a
liquid or hydraulic pressure which will actuate a piston and piston
rod to move in either of two directions; extend or retract.
For purposes of description herein the device will be described as
driven by a direct current motor controlled by a three position
switch or relay by which current is directed appropriately to yield
motor shaft movement either clockwise, counterclockwise, or stop or
at rest position.
More particularly the present invention relates to a novel and
unique pump which is bi-rotational. By bi-rotational is meant a
pump that has two pressure outlets connectable to opposite ends of
a hydraulic cylinder containing a movable piston rod and piston
therewithin capable of moving in directions as controlled by the
pumps rotational movement. As indicated above the pumps rotational
direction is herein described as effected by a direct current
electric motor whose drive shaft rotation is dependent upon the
electrical connection effected by the three-position switch or
relay. Reversing polarity will reverse rotation. As can be
appreciated the to and fro motion of the piston rod is of utility
in effecting controlled reciprocal movement of a variety of
elements as more particularly and detailedly described
hereinafter.
The present invention relates most particularly to a hydraulic
bi-rotational pump embodying novel feature of structure and
operation which allows achievement and simplicity of operation
beyond that anything known at the present time; and being capable
of being constructed very small which permits its utilization in a
manner unknown to the present time.
Gear pumps, of course, are well known in the art and need no
present detailed description. Gear pumps are generally constructed
of two intermeshing gears located in a cavity having an inlet and
an outlet. In the gear pump of the present invention the structure
is of such novelty and unique design as provide an inlet for the
pump in the usual fashion but in accordance with the present
invention has two outlets. One outlet is used to convey hydraulic
oil or develop pressure through one outlet, depending on a
clockwise rotation of the motor and the connected shaft on which is
mounted the intermeshing gear. The other outlet is used to direct
fluid pressure pursuant to counterclockwise rotation of the DC
motor shaft and the connected drive shaft bearing the gears and
controlling the movement and rotation of the intermeshing
gears.
The novelty of the present pump may be described as due in part to
its constructional details consisting of multiple parts located in
flush side by side relationship; on either side of the housing
containing the intermeshing gears; said side by side parts being
machined to contain a novel arrangement of internal passageways
interrupted by moveable ball type check valves and piston actuated
valves; all operating in cooperative relationship to direct the
appropriate fluid, usually a hydraulic oil, out one or the other of
the two outlets connected by appropriate passageways/conduits to
opposite ends of a cylinder or actuator containing the usual piston
rod and piston arrangement.
The construction is such that instant and positive change of
direction of the piston is achieved by appropriate actuation of the
drive motor and controlled by the three-position switch,
accomplishing appropriate direction of the hydraulic fluid to one
side or the other of the piston in the actuator cylinder. The
design and interrelationship of these cooperating parts and
features are such that the entire pump body is surrounded by the
hydraulic fluid and the size of the pump is extremely small (as
described in more detail hereinafter) such that it can be
fabricated of a large selection of materials of construction
(aluminum preferred) and of a size as permits desired utilitarian
functionality in a variety of applications.
While the pump of the present invention may be
fabricated/constructed of a variety of materials including metals,
engineering plastics, acrylonitrile/butadiene/styrene (ABS)
tripolomers, etc.; aluminum is a preferred material of construction
for the pump parts identified hereinafter, with the exception that
the oppositely rotatable intermeshing gears and their cavity
wherein located is usually desirably formed of steel by reason of
its being able to endure the frictional movement of the counter
rotating gears within the cavity. The pump of the present invention
is desirably fabricated, at the present time (as a preferred mode),
to an overall dimension of about two inches (2") in length by about
one and one quarter inches (1-11/4") in diameter.
This is remarkably small considering the many unique and
sophisticated, constructional details including the passageways
which are integral to a successful operation and to the small ball
and check valves (with opposing springs in some cases), as also
described herein. A currently suitable and appropriate direct
current motor may be selected from a variety of generally
available, direct current motors whose shaft rotation is dependent
upon the electrical connection to the positive and negative
terminals.
It is a variant embodiment of the present invention to employ the
bi-rotational pump and suitable drive motor by locating both within
a hydraulic cylinder/actuator. The latter will also include a
piston and piston rod driven/movable by the hydraulic pressure
developed by the rotation of the intermeshing gears in the novel
bi-rotational pump. The latter as described earlier and illustrated
in the drawings includes two outlets which, by reason of the
passageways formed in the pump on either side of the gear housing,
direct fluid through appropriate passageways, to one side or the
other of the piston slidably located in the actuator, so as to
accomplish a linear reciprocating movement in turn depending upon
the connection (via switch or relay) of the electric direct current
to one or the other terminals of the motor. The latter, of course,
will result in the rotating of the gears in one direction or then
other thus so that pressure will be developed within the pump
proper as to direct the hydraulic pressure via outlets/passageways
to either one side or the other of the piston.
It will be appreciated that the hydraulic driving gear rotates
directly as driven by the shaft of the direct current motor. A
cooperating sister gear in intermeshing relationship with the
principal driving shaft is mounted on a idler shaft located in
parallel relationship with the drive shaft as above.
In accordance with a subsidiary embodiment of the present
invention, the bi-rotational hydraulic pump is employed in
combination with an actuator, and an electric motor driving the
bi-rotational hydraulic pump, all located within the hydraulic
cylinder, including provisions for an oil reserve, and forming one
compact unit. This unit yields a package with no leaking
connectors, no valves to operate and no maintenance over its life.
The oil reserve reservoir has no connection with the outside air so
no oil will be able to escape through a vent. All exposed material
is aluminum except for the piston rod which is fabricated of
Nitrotech steel and the electric motor.
In summary, the actuator operates as follows: when the electric
D.C. Motor is rotating clockwise, the piston rod is extending from
the hydraulic cylinder or actuator. When the motor is rotating
counterclockwise, the piston rod is retracting into the actuator
cylinder. When the electric motor is off the piston rod is
hydraulically locked into position.
The combination of motor, pump, fluid reservoir and cylinder in a
single package has very unique utility in constituting therefore a
self-contained actuator requiring only a change in the polarity of
the motor to achieve a change in the direction of the bi-rotational
pump and, through its novel arrangement of passageways and ball
valves, a change in the direction of the hydraulic flow such that
it passes into the actuator cylinder on one side of the piston or
the other.
In this fashion the movement of the piston rod is reversed to
effect appropriate movement of the mechanism part or item which is
desirable moved reliably in reciprocal, to and fro fashion.
A unique and novel feature and utilitarian feature is that the
totality of the cylinder, of the motor and the pump in accordance
with the present invention weighs little more than a conventional
hydraulic cylinder for the same application.
This embodiment of the present invention wherein the novel
bi-rotational pump, the hydraulic cylinder and including the drive
motor in one cylinder finds particular utility in the field of
recreational vehicles to control the sliding/reciprocating movement
of rooms or levelers or letdown shades etc.
It can also be used in the transportation field eg. cars, vans,
buses and including paraplegic lifts. The cylinder, referred to as
an actuator, is also usable in lift gates, cranes, and support legs
in the truck equipment business.
In the general field of industry the bi-rotational pump and
reciprocal piston rod finds its utility as a door closer, as an
opener of skylights, and in positioning fixturing, materials
handling. Further in the field of automotive and specifically
garden tractors the device is used in deck lifts as well as
three-point hitch lifts. In the field of material handling, the
device, in the form of the reciprocable piston controlled by
hydraulic fluid described hereinabove and in more detail
hereinafter finds utility in controlling belt lifts, material
clamping, scissors lifts, as well as conveyor control.
In the marine environment these devices find wide acceptance in the
field of driving of tilt trims, trim tabs, or the opening of
skylights, etc. In the field of agriculture the device is eminently
utilitarian in the control of support legs, auger control, gate
closers, and implement lifts.
Presently available gear pumps are largely unsuitable in the
applications described, by reason of their larger size, heavier
weight, and their general inaccuracy and lack of close control as
compared to the bi-rotational pumps of the present invention and as
compared to the combination of the bi-rotational pump and actuator
and electric motor in one compact cylinder as described herein.
OBJECT
With the foregoing introduction it is a principal object of the
present invention to provide a novel and unique bi-rotational pump
of such features of construction as allow it to be produced in
extremely small sizes.
It is another object of the present invention to provide such a
novel pump which by reason of the range of materials of
construction allowable by reason of the design of the present
invention permits the pump to be manufactured to extremely close
tolerances which results in considerable savings of weight yielding
a pump which is lighter than provided by the conventional pumps of
the present art.
It is a further object of the present invention to provide
combinations of the bi-rotational pump with other hydraulically
driven systems as do not presently exist on the market today.
It is a further object of the present invention to provide a
bi-rotational multi-component pump having features of interior
structure inclusive of passageways and means controlling flow of
fluid in these passageways which extrapolates to a balancing of
hydraulic forces axially and radially acting on the pump interiorly
and exteriorly. Thus less material is needed for a structurally
sound pump than what has been possible with prior art pumps. This
results in a much smaller and lighter pump. Thus normally the gear
housing must be made or fabricated of a greater wall thickness
whereby weight is greater than with the design of the present
invention.
It is still another object of the present invention to provide a
modified bi-rotational pump device which is extremely utilitarian
and capable of being associated with and combined with a diverse
variety of cooperating mechanical components and electronic
components such as to improve the functioning of the cooperating
mechanical components eg. exhibiting reciprocal movement.
The foregoing objects and, as well, other objects of the present
invention will become apparent to those skilled in the art from the
following detailed description, taken in conjunction with the
annexed sheets of drawings inconclusive of eighteen (18) FIG,
labeled FIGS. 1-18 and supplemental drawings, labeled FIG. 19, FIG.
20, FIG. 21 and FIG. 22. FIGS. 1 thru 18 exist for purposes of
illustration only and not to limit the scope of the invention. In
other words, the Figures illustrate preferred embodiments of the
present invention that are not to be interpreted as limited unless
violative of the scope of the claims appended to this
Application.
FIGS. 3, 4, 5, and 6 illustrate schematically the functional
operation of the present invention from a hydraulic point of
view.
FIGS. 7 thru 18 illustrate the present actual best mode of the many
embodiments of the present invention in term of actual
constructional details which are desirable for purposes of
achieving the objects of the present invention as set forth herein,
and, as well, other manifestly obvious alternatives and
equivalents.
IN THE DRAWINGS
FIG. 1 is a side elevation view of an actuator assembly including a
direct current motor, a bi-rotational pump, in accordance with a
preferred embodiment of the present invention, and the
axially-connected hydraulic actuator cylinder shown in a retracted
position.
FIG. 2 is a perspective and partially broken away, view of the
assembly shown in FIG. 1.
FIG. 3 is a schematic drawing showing the pump and actuator
components of FIGS. 1 and 2 in perspective relationship, but
displayed in spaced apart relationship for purpose of illustrating
the flow of hydraulic fluid and its intended purpose of actuating
the actuator via the bi-rotational pump movement/pressurization of
the hydraulic fluid. The pump and actuator components of FIG. 1 and
2 are shown fluidly connected.
FIG. 4 is a schematic view of the components of FIG. 3 but being a
sectional rendition for purposes of showing the interior of the
pump and actuator situated thereabove and particularly the
relationship of the bi-rotational pump parts or components
including its interior ball valves, check valves, etc., etc.,
controlling the direction of flow of fluid, via the ball valves,
check valves etc. positioned as shown. In this position the pump is
locked, as indicated on the drawings and, of course, the hydraulic
cylinder and piston are also locked.
FIG. 5 is a view like FIG. 4 but with the component parts e.g. ball
valves, check valves, etc. shown in operative relationship/fashion
for actuating the piston into its retracted position.
FIG. 6 is a sectional view like FIGS. 4 and 5 but with the
component parts e.g. ball valves, check valves, etc. shown in
operative relationship/fashion for actuating the piston into its
extended position.
[In FIGS. 4, 5 and 6 the movement of the piston in the cylinder or
actuator is opposite to that illustrated in FIG. 2.]
FIG. 7 is a sectional view taken on the Line 7-7' of FIG. 15.
FIG. 8 is a sectional perspective view taken (on the Line 8-8' of
FIG. 7) and is a view of the top one half of the pump held between
pump retainers as described more particularly hereinafter.
FIG. 9 is an enlarged vertical partially sectional) view of the
left one half of the apparatus shown in FIG. 1, and particularly
showing the interior of the pump and its surrounding
components.
FIG. 10 is a view like FIG. 9 but is of the right-hand segment of
the apparatus shown in FIG. 1.
FIG. 11 is a perspective view of the pump parts located at the
drive end or left side of the pump and being shown in relative
exploded relationship for clarity of illustration.
FIG. 12 is a perspective view of the component parts of the right
hand side of the pump shown in relative exploded relationship for
clarity of illustration.
FIG. 13 is a perspective view of the left side end cap with certain
parts shown in exploded relationship for purposes of clarity of
illustration.
FIG. 14 is a perspective view similar to FIG. 13 and of the pump
cover on the left-hand side of the pump and with certain parts
shown in exploded relationship for clarity of illustration.
FIG. 15 is a sectional view, somewhat enlarged, of the pump proper
taken on the Line 15-15' of FIG. 7 and is somewhat duplicative of
the parts shown in FIG. 8.
FIG. 16 is a sectional view taken on the Line 16-16' of FIG. 15 for
the purpose of showing the intermeshing gears located in the cavity
formed in the gear housing.
FIG. 17 is a somewhat enlarged perspective view like, FIG. 14 but
of the right hand cover member of the bi-rotational pump.
FIG. 18 is an enlarged view of the end cap on the right side of the
bi-rotational pump assembly and accordingly somewhat similar to
FIG. 13 but of the cap at the opposite end or on the other side of
the gear housing and gear assembly.
FIG. 19 is a sectional view of the pump showing the valve position
and the relative direction of flow of fluid during each of three
positions locked, extended and retracted.
FIG. 20 is a dimensional drawing of an actuator according to the
present invention.
FIG. 21 is a graph of an actuator performance of the present
invention in which the weight in pounds is located on the abcissa
and the stroke in inches is located on the ordinate.
FIG. 22 is a graph of the same device representing the best mode of
the present invention in speed and inches per second.
For convenience, the following Tables identify the above individual
FIGURES and list the drawing numerals to the corresponding
part.
FIG. 1 #1a D.C. Motor #2a Pump #3a Actuator/Cylinder #4a Piston Rod
#3b Actuator Cylinder Assembly FIG. 2 #1a D.C. Motor #5a Relay or
Manual Switch #6a Passage (Pump to piston cylinder to extend) #7a
Passage (Pump to Piston Cylinder for Retract) #4b Piston #9a
Cylinder For Piston #4a Piston Rod #8a Passage (Reservoir To Pump
Inlet) #2a Pump #13a Reservoir #45 Guide End #41 Seal FIG. 3
SCHEMATIC #4a Piston Rod #4b Piston #3a Actuator Cylinder #10a
Extend #11a Retract #6a Passage To Piston Cylinder For Extend #2a
Pump #8a Reservoir To Pump Inlet #13a Reservoir #14a Pump Cylinder
End Cap #15a Pump Lower Chamber #16a Pump Upper Chamber #7a Passage
To Piston Cylinder To Retract FIG. 4 SCHEMATIC (LOCKED POSITION)
#4a Piston Rod #3a Cylinder #4b Piston #35 Drive Shaft Stationary
#18a Check Valve (Closed) #19a Pilot Piston #20a Check Valve (No
Spring-Closed) #21a Check Valve (Open) #2a Pump #13a Reservoir #14a
Pump Cylinder End Cap #23 Check Valve (Closed) #24 End Cap #25
Pilot Piston #26 Cover #34 Gear Housing #28 Check Valve (No
Spring-Closed) #29 Cover #30 Check Valve (Closed) #31 End Cap #15a
Pump Lower Chamber #16a Pump Upper Chamber #8a Passage Reservoir To
Pump Inlet FIG. 5 SCHEMATIC (RETRACTED POSITION) #4a Piston Rod #3a
Actuator #4b Piston #18a Check (Open) #32 Pilot Piston #20a Check
Valve (No Spring-Closed) #21a Check Valve (Open) #2a Pump #13a
Reservoir #14a Pump Cylinder End Cap #23 Check Valve (Closed) #24
End Cap #25 Pilot Piston #34 Gear Housing #28 Check Valve (No
Spring-Open) #29 Cover #30 Check Valve (Closed) #31 End Cap #35
Drive Shaft #8a Passage Reservoir To Pump Inlet #6a Passage To
Piston Cylinder To Extend #7a Passage To Piston Cylinder To Retract
FIG. 6 SCHEMATIC (EXTENDED POSITION) #4a Piston Rod #3a Actuator
#4b Piston #35 Drive Shaft (Moving Clockwise) #18a Check Valve #19a
Pilot Piston #20a Check Valve (No Spring-Open) #21a Check Valve
(Closed) #2a Pump #13a Reservoir #14a Pump Cylinder End Cap #23
Check valve (Open) #24 End Cap #25 Pilot Piston #26 Cover #34 Gear
Housing #28 Check Valve (No Spring-Closed) #29 Cover #30 Check
Valve (Open) #31 End Cap #6a Passage to Piston Cylinder to Extend
#7a Passage to Piston Cylinder to Retract #8a Passage reservoir To
Pump Inlet FIG. 7 MOTOR END OF PUMP WITHOUT PUMP RETAINER #35 Drive
Shaft #37 Idler Shaft #4c Motor End of Pump (Without Pump Retainer)
FIG. 8 TOP ONE HALF of PUMP WITH RETAINER #35 Drive Shaft #39 Pump
Retainer #18a Check Valve #2a Pump #31 End Cap #29 Cover #26 Cover
#24 End Cap #25 Pilot Piston #20a Check Valve (No Spring) #21a
Check Valve #23 Check Valve #19a Pilot Piston #40 Gear Only #2a/39
Pump with Pump Retainer #28 Check Valve (No Spring) #30 Check Valve
#39a Pump Retainer #35 Drive Shaft FIG. 9 1a Motor #35 Drive Shaft
to Motor #40 Gear #6a Passage (pressure to extend) #4a Piston #4b
Piston Rod #7a Passage to Piston Cylinder to Retract #41 Seal #24
End Cap #13a Oil Reservoir #8a Passage Inlet #14a Pump Cylinder End
Cap #37 Idler Shaft #26 Cover #2a Pump #42 Gear #29 Cover #43 Pump
Retainer #31 End Cap FIG. 10 #6a Passage to Cylinder for Extend #44
Plug #4a Piston Rod #45 Guide End #9a CYL for Piston Rod #13a Oil
Reservoir #45a O-Ring FIG. 11 DRIVE END PARTS #46 Opening #31 End
Cap #29 Cover #47 Dowel Pin #35 Drive Shaft #37 Idler Shaft #48
Dowel Pin #25 Pilot Piston #49 Outlet FIG. 12 #35 Drive Shaft #47
Dowel Pin #50 Gear Key Ball #40 Gear #34 Gear Housing #21a Pilot
Piston #26 Cover #28 Check Valve (In Place) #24 End Cap #6a Opening
#18a Check Valve (In Place) #20a Check Valve (No Spring) #42 Gear
#48 Dowel Pin #53 Gear Key Ball #37 Idler Shaft FIG. 13 (END CAP)
#46 Opening #7a Fluid Passage to Cylinder to Retract #54 Hole For
Dowel Pin #30 Check Valve #55 Hole For Dowel Pin #49 Outlet Fluid
Passage #56 Check Valve Seat #18a Check Valve #56a Check Valve
Seats #31 End Cap FIG. 14 (COVER) #7a Fluid Passage to Cylinder to
Retract #60 Hole For Idler Shaft #7a Fluid Passage #54 Hole For
Dowel Pin #58 Hole For Drive Shaft #20a Check Valve (No Spring) #55
Hole For Dowel Pin #19a Pilot Piston #29 Cover FIG. 15 PUMP #2a
Pump #39 Pump Retainer #46 Opening #35 Drive Shaft To Motor #31 End
Cap #29 Cover #34 Gear Housing #26 Cover #24 End Cap #40 Gear #58
Gear Key Ball #6a Opening #59 Gear Key Ball #42 Gear #37 Idler
Shaft FIG. 16 #42 Gear #7a Fluid Passageway #53 Gear Key Ball #40
Gear #34 Gear Housing #61 Dowel Pin #35 Drive Shaft To Motor #50
Gear Key Ball #48 Dowel Pin #7a Fluid Passageway #37 Idler Shaft
FIG. 17 (Cover) #7a Fluid Passage #60 Hole For Idler Shaft #20a
Ball Valve (No Spring) #46 Fluid Passage #25 Pilot Piston #54 Hole
For Dowel Pin #62 Drive Shaft #55 Hole For Dowel Pin FIG. 18 END
CAP #53 Ball Valve #50 Ball Valve #7a Fluid Passage #54 Hole For
Dowel Pin #6a Opening
#55 Hole For Dowel Pin #7a Fluid Passage FIG. 19 #3a
LOCKED/Actuator hydraulically locked into position #2a/10a
EXTEND/Pump rotating clockwise #2a/11a RETRACT/Pump rotating
counterclockwise FIG. 20 #63 (2) 3/8-16 UNC 0.375 DEEP #64 .O
slashed..625 2.500 ACROSS COUNTER SINKS #65 .O slashed..625 #66 ROD
END PER CUSTOMER SPECIFICATIONS #67 5.72 + STROKE #68 5.09 + STROKE
#70 3.75 MOTOR M300-1 3.82OTOR M300-2 #71 .O slashed.2.50 FIG. 21
ACTUATOR 125-35 Force, Speed Current Draw #72 Force No's. #73
Speed, in/sec #74 Force extend #75 Force Retract #76 Speed Extend
#77 Speed Retract #78 12 Volt DC FIG. 22 #3a ACTUATOR 125-035
WEIGHT #79 WEIGHT, LBS #80 STROKE, IN
In its simplest embodiment, the present invention contemplates a
bi-rotational gear pump comprising a generally circular gear
housing having a generally central cavity contoured for a pair of
intermeshing gears carried concentrically respectively on a drive
shaft and a parallel idler shaft spaced from said drive shaft
sufficiently to allow intermeshing rotation of said gears in either
direction to move fluid in either direction; a pair of generally
circular cover members situated concentrically in flush abutment on
either side of said gear housing and a pair of generally circular
end cap members in concentric flush abutment on either side of said
cover members; said cover members and end cap members, on either
side, containing a series of connected internal passageways and
defining one inlet fluidly connected to said intermeshing gears,
and two outlets, one for each rotational (clockwise or
counterclockwise) movement of said intermeshing gears. The outlets
are adapted for fluid connection with a hydraulic cylinder on
either side of a piston and connected piston rod, the latter being
reciprocal. Said passageways include a plurality of ball/check
valve means constructed and arranged (together with appropriate
valve seats) to control/direct fluid to one or the other of said
outlets depending upon the rotational movement of said intermeshing
gears in clockwise or counterclockwise (or stationary position) and
means enclosing said bi-rotational pump such that the pump parts
are surrounded by the fluid being pumped, said fluid exhibiting the
pressure developed by the pump itself.
In accordance with a further embodiment of the present invention
the pump includes means for directing said pumped fluid through
either of said outlets, depending upon the rotation of the pump,
and then via appropriate passageways/conduits to a hydraulic
cylinder or actuator containing a linear shaft and connected piston
moving in either direction responsive to the fluid introduced into
the actuator interior; and further characterized in that said
bi-rotational pump is carried in a surrounding shell defining a
space or volume/reservoir fluidly connected to said passageways of
said pump formed in said cover and end cap members and including
the conduit direction of fluid from either of said aforesaid
outlets to the corresponding actuator cylinder.
According to another embodiment of the present invention, the pump
includes means connected thereto for mounting same in an actuator
cylinder in generally coaxial relationship with the piston rod and
the shaft of an electrically driven motor controlled by a three
position switch or relay such that the motor will remain at rest or
will rotate in one direction and then the other direction
responsive to said switch or relay position. The switch (relay) may
be manually controlled or any timer or other means.
DESCRIPTION
Referring now specifically to the drawings, there is disclosed in
FIG. 1, a side elevation view of a actuator/cylinder assembly (3b)
inclusive of a electric motor (1a) at one end, a piston (4b) and
piston rod (4a) assembly at the other end, and intermediate, a
bi-rotational pump (2a) in accordance of the present invention.
FIG. 2 is a perspective view, of the elements of FIG. 1, with
portions broken away, for the purpose of showing the interior
positioning of the pump (2a) in the actuator/cylinder (3a) and the
flow of fluids, usually hydraulic oil, in the actuator (3a), piston
(4a) and cylinder (9a) and the surrounding annular void (13a)
serving as an oil reservoir. Also shown are passageways leading
from reservoir (13a) via an inlet (8a) to the pump (2a) and outlets
(6a, 7a) fluidly leading to one side or the other of the piston
(4b) axially disposed in the actuator (3a).
For purposes of clarity FIG. 3 is schematic in that the
bi-rotational pump (2a) and its reservoir enclosure (13a) and the
actuator cylinder (3a), including piston rod (4a) and piston (4b)
are shown in distinct, spaced relationship. The reservoir (13a) is
connected to bi-rotational pump (2a) by an inlet (8a) leading to
the interior of the pump (2a). The pump (2a), depending on the
clockwise (cw) or counterclockwise (ccw) direction it is rotating,
discharges pressurized fluid to the upper (16a) or lower (15a)
chamber of the pump enclosure and then, by suitable Internal
passageways, to the actuator cylinder (3a) thereabove, to which it
connects on either one side or the other of the piston which moves
the piston rod (4b) to and fro to the left and to the right
depending on the hydraulic pressure developed by appropriate
rotational movement of the gears (not shown).
FIG. 4, as noted in TABLE X, represents a "no rotation" position of
the drive shaft (35) and wherein valves (23), (18a), (21a) and (30)
are closed. They are closed because with "no rotation" of the
driveshaft (35) there is no pressure in either chamber (15a) or
(16a) to actuate the pilot pistons (19a) of (25), either of which
would open the corresponding valves (18a) or (23) respectively.
Likewise valves (30) and (21a) are closed and held closed by the
spring as shown because there is no pressure to overcome the
resistance of the spring holding the respective valves (30) and
(21a) in the closed position. The closed position represents a
locked position.
The accompanying FIG. 19 illustrates the valve positions and flow
of fluid respecting FIGS. 4, 5, and 6.
Referring to FIG. 5 the position of the parts such as ball valves
etc. are the result of counterclockwise (ccw) movement of the pump
shaft (35) whereby pressure is developed in the lower half (15a) of
the pump (2a) and moves fluid up the left outlet to the interior of
the cylinder/actuator (3a) causing movement of the piston (4b) and
connecting rod (4a) to the right to the retract position. At the
same time the hydraulic fluid on the other side of the piston (4a)
is moving downwardly to the upper chamber (16a) and through the
pump (2a) in a manner illustrated by the arrows and open position
of the ball valves (28, 18a, 20a) and the arrows and the closed
position of ball valves (23, 30, 20a).
Referring now to FIG. 6 and TABLE X, the drive shaft (35) is
rotating in a clockwise (cw) direction of rotation, which is the
reverse of the counterclockwise (ccw) direction shown in FIG. 5.
This change in direction of rotation results in a pressure being
immediately urged against pilot piston (25), which moves downwardly
against spring opposed ball (23), thereby opening the associated
valve (23) and in addition valves (30) and (20a) as shown. The
continued clockwise (cw) rotation of the drive shaft (35) also
closes ball valves (28, 18a, 21a). And as a consequence there is a
change of pressure whereby the pressure is greater in the fluid
flow into upper chamber (16a) causing the fluid to flow out conduit
(7a) upwardly into the actuator (3a) to the left of piston (4b)
causing piston (4b) to move to the right into the retract position.
This in turn moves liquid out of the opposite end of the actuator
(3a) down conduit (6a) into the lower chamber (15a) and through
valve (23) to the reservoir (13a) thereby initiating a reversal to
the FIG. 5 conditions by reason of changing the rotation of pump
(2a) from clockwise (cw) to counterclock (ccw).
It my be stated at this juncture, that it is a particular feature
of the present invention that the entire system is essentially
filled with fluid, such that the hydraulic pressure is the same
throughout thus supporting the exterior surfaces of the pump (2a)
whereby the pump components may be made smaller structurally
through the support of the surrounding fluid and the hydraulic
pressure developed therein. The pump may be mounted in a block of
such a small size, which was not possible with prior art.
It is this feature that allows the pump structure (2a) to be made
so small as to fit within the actuator cylinder (3a) rather than
exteriorally as in the usual case in the art as of today.
With the understanding gained by the foregoing hydraulic
language/description, relative to FIGS. 1 thru 6; it is believed
that the remainder of the Figs., particularly FIG. 7 through 18,
will be readily understood by referring to the drawings. Thus the
drawings in FIGS. 7 through 18 are based upon and illustrate
actual, individual component parts and assemblies, but shown about
3 times larger than actual size. In these specific drawings, it is
recommended that FIG. 7, FIG. 8 and FIG. 15 be viewed together and
which respectively show an end view and sectional views of the pump
proper (2a) showing the motor drive shaft (35) and the parallel
spaced idler shaft (37). In FIGS. 8 and 15 the gears (40/42) and
gear housing (34) have flushly situated, on either side, cover
members (26/29) and outward of the cover members (26/29) are
flushly situated end cap members (31/24) left and right.
FIG. 15 shows gear key balls (58/59) serving as a lock key securing
the gears (40/42) to the drive shaft (35) and idler shaft (37) thus
turns the gears (40/42) in a clockwise (cw) or counterclockwise
(ccw) rotation. The pump (2a) components consisting of gears
(40/42), and covers (26/29) and end caps (31/24) members on either
side of gear housing (34).
Referring to FIG. 9, the oil reservoir (13a), via the inlet
(passage 8a), as connected fluidly to the central portion of the
pump (2a), as quite clearly illustrated; as are the outlets
respectively identified as passageway (6a and 7a). Now as shown in
FIGS. 2 and 9, passage (6a) connects the outlet of the pump (2a) to
the actuator cylinder (3a) on the extended side of the piston (2a)
to achieve extension of the piston rod (4b); while passage (7a)
connects the pump outlet assuming counterclockwise (ccw) movement
of the drive shaft) to carry the liquid to the cylinder, as shown,
at the extremity of the cylinder to achieve movement of the
piston/shaft (4b/4a) to the left and thus in a retracting
movement.
FIG. 8 is a sectional view of the top half of the pump (2a) and
shows clearly the pump retainers (14a/39) at each end and
exteriorly of the end cap members (31/34).
FIG. 10 shows the oil reservoir spaces (13a) surrounding the piston
rod/cylinder (9a) and the journeling of the right or terminal end
of the piston rod (4a) and the outer end (6a) of the cylinder (9a).
This Fig. also shows passage (7a) delivering hydraulic fluid under
pressure to the terminal end of the piston rod (4a) and cylinder
(9a) arrangement. These parts are shown generally in fluid sealed
relationship mounted in the guide end (45) identified in FIG.
10.
FIG. 11 shows in detail the relationship of the generally circular
and coaxially mounted end cap (31) and cover (29) with the openings
for the drive shaft (35) and idler shaft (37) as well as the
registration-locating dowel pins (47/48).
FIG. 12 is like FIG. 11 but shows the component parts particularly
the gear housing (34), the right hand cover (26) and right hand end
cap (24), in exploded perspective view, to show the dowel pins
(47/48), the idler shaft (37) and the drive shaft (35) the gears
(40/42), and a passageway (6a) for the fluid. Ball type check
valves (28 and 18a), the pilot piston (21a) and check valve with no
spring (20a) are also shown in FIG. 12 due to the exploded nature
of the drawings.
FIG. 13 is also an exploded view, somewhat enlarged, of the left
side end cap (31) and the opening (46) necessary to accommodate the
drive shaft (35), and idler shaft (37) and openings (54/55) for
dowel pins (47/48) respectively. FIG. 13 also shows the outlet
fluid passage (49).
FIG. 14 is like FIG. 13, that is, exploded, and shows the left hand
cover member (24) and, as well, a pilot piston (19a) and the
spring-opposed ball check valve (20a).
FIG. 16 shows the gear housing (34) and the gears (40/42) as well
as the lock balls (50/53), serving as keys, connecting gears to the
shafts (35/37) and as well the dowel pins (61/48) location for
registration of these component parts flushly together.
FIG. 17 is useful in understanding the construction of the right
hand cover member (26) adjacent the gear housing (34), and, as
well, the holes (54/55) for seating the dowel pins for registration
plus the machined holes (60/62) for the drive shaft (35) and idler
shaft (60) are shown.
In FIG. 18 there is shown, in enlarged perspective, the right hand
cap member (26). This Figure is also noteworthy, in illustrating
the inlet fluid passageway (7a) and the outlet fluid passage (7b)
for the fluid caused by the rotation of the gears (40/42) and
directing fluid under pressure as indicated in FIG. 2 to the outer
or terminal end of the actuator (3b).
This basic pump design can be as a single rotational pump with one
output flow, where all check valves and pilot pistons are deleted.
This pump would be very light and compact. See sketch provided with
the material with the application.
Hereinabove, considerable focus, attention and description has been
placed upon the embodiment of the invention comprising the double
acting bi-rotational pump in combination with piston and cylinder
actuator; but it should be appreciated that the bi-rotational pump
has considerable utility and application for use in and of itself.
The bi-rotational pump enclosed in a suitable jacket or enclosure,
including means defining voids for use as a reservoir will find
many applications wherein the direction of the pump is maintained
almost exclusively in either clockwise movement of the gears as
directed by the electric motor or in counterclockwise movement.
To do this it will be necessary to supply a continuing supply of
hydraulic fluid or arrange for some of the fluid exiting one of the
outlets to be re-circulated to the inlet. Thus the pump could be
used for incremental movement of fluid in one direction only by use
of an electric switch or relay which has simply 2 positions; an at
rest position and a clockwise or a counterclockwise position. Such
a pump would have all the advantages of a gear pump plus the
additional advantages provided by the present gear pump in having
its pressure exerted on its outside surfaces as well as in the
internal conduits.
Along with this advantage would be the miniaturization of the
components which would be available due to the feature of the
bi-rotational pump as described hereinabove.
It would of course also be possible to plug or delete the
passageways leading to one of the outlets. In this fashion there
would only be one outlet which could be directed through
appropriate conduit to any destination desired. One example would
be to enclose the bi-rotational pump with one outlet plugged into a
conduit with suitable arrangements for direct current rotation of
the drive shaft. A plurality of such arrangements would provide
pumping energy to be exerted upon fluids to be conveyed a long
distance more efficiently than with a single gear pump located at
the inlet end of the conduit under consideration.
From the foregoing drawings, and the general and specific
descriptions, it will be appreciated that significant advantageous
features of the present invention reside in the unique design of
the multi-component gear pump; including its coaxially mounted
members on either side, which provide/include flow of fluid in
different directions by reason of a unique selection and
arrangement of spring opposed-ball check valves and ball check
valves which are not spring opposed. These are arranged in a novel
fashion to define different flows of fluid as controlled by the
position of ball check valves and certain pilot pistons controlled
by a ball check valve which are not spring opposed. All of these by
their location and control cooperate to provide a flow of fluid and
corresponding pressure in one direction or the other depending on
the rotation of the drive shaft of the pump controlled in turn by
an electric motor, having controlled to off, on right, or on, on
the left.
This combination of features provides reliable and positive
reversible rotation of the gear pumps and by reason thereof a
reversible flow of fluid for example, to different sides of a
piston in a piston driven mechanism all in a manner not known
heretofore in the art.
Compounding these features is that they provide a reduction in the
size, as noted in the Specification hereinandabove, which suggests
and promotes its usage in a wide variety of hitherto
unknown/unrealized applications.
From the foregoing description, specification and in combination
with the drawings; it will be appreciated that many obvious changes
and modifications will become apparent to those skilled in the art
and all those obvious modifications and changes are intended to be
included within the scope of the present invention unless such
would do violence to the scope of the appended claims.
* * * * *